JP2001121904A - Wheel bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To inhibit the lopsided wear and brake judder of a brake rotor in consideration of other causes of the surface vibration of the brake rotor than the improved precision of unit parts. SOLUTION: A bearing 4 comprises an outer ring 15 having plural lines of raceway surfaces 16, 17 on the inner periphery, a hub rang 1 in which inner rings 20, 21 having raceway surfaces 18, 19 opposed to the raceway surfaces 16, 17 thereof are pressed, and plural lines of rotors 22, 23 laid between the outer ring 15 and each of the inner rings 20, 21, wherein a wheel mounting flange 31 is provided on the hub ring 1 and an outward joint member 3 of an equal-speed universal joint 2 is fitted to its inner diameter. Pre-load is granted to the bearing 4 and the hub ring 1 is integrally joined to the outward joint member 3 of the equal-speed universal joint 2 with given axial tension or more by using a nut 9.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a wheel bearing device, and more particularly to a wheel bearing device capable of rotatably supporting a front wheel of an FF or FR vehicle on a vehicle body and suppressing uneven wear of a brake rotor and brake judder. .

[0002]

2. Description of the Related Art A bearing device for rotatably supporting a drive-side wheel of a front-wheel drive vehicle includes a hub wheel, an outer joint member of a constant velocity universal joint, and a bearing. The outer joint member of the constant velocity universal joint has a stem portion extending in the axial direction inserted into the through hole of the hub wheel, and the outer ring of the stem portion and the serration formed on the inner diameter of the through hole form a connection with the hub wheel. They are connected so as to be able to transmit torque and are fixed with nuts.

This bearing device has a structure in which a hub wheel is rotatably supported by a bearing such as a double row angular contact ball bearing, and a wheel wheel is fixed to the hub wheel, and the bearing is suspended via a knuckle. Supported by device. The outer ring of the bearing is bolted to a knuckle via a flange protruding from the outer periphery of the outer ring of the bearing. The hub wheel has a flange, and the brake rotor is fixed to the flange by a hub bolt for fixing the wheel.

[0004] With respect to the bearing device for rotatably supporting the driven wheel of the FR vehicle, except for the outer joint member of the constant velocity universal joint in the bearing device for the driving wheel described above.
There is a unit in which a hub wheel and a bearing are unitized, or an outer ring rotating type in which a wheel mounting flange is provided on the outer periphery of the outer ring.

[0005]

By the way, generally,
In the wheel bearing device, when a run-out (axial run-out) occurs in the brake rotor attached to the flange of the hub wheel, it may cause vibration during braking from a high-speed driving of the automobile, and may cause uneven wear of the brake rotor and brake. A judder problem occurs. In order to prevent uneven wear of the brake rotor and brake judder, it is necessary to suppress the runout of the brake rotor.However, in order to suppress the runout of the brake rotor, the runout of the mounting surface of the brake rotor alone is reduced. In addition to suppression, it is necessary to suppress flange runout of the hub wheel alone, axial runout of the bearing, assembly error (misalignment), and the like, and it is necessary to improve the accuracy of each component alone.

However, as described above, in addition to the run-out of the mounting surface of the brake rotor alone, the flange run-out of the hub wheel alone, the axial run-out of the bearing, and the assembly error (misalignment) are suppressed to improve the accuracy of each component alone. However, it is difficult to completely prevent uneven wear of the brake rotor and brake judder.

Accordingly, the present invention has been proposed in view of the above problems, and its object is to focus on other factors that cause the runout of the brake rotor besides improving the accuracy of each component alone. Another object of the present invention is to provide a wheel bearing device capable of further suppressing uneven wear of the brake rotor and brake judder.

[0008]

As a technical means for achieving the above object, the present invention provides an outer member having a plurality of rows of raceways on its inner periphery, and a raceway surface opposed to each of the raceways. An inner member having a bearing comprising a double row of rolling elements interposed between the outer member and the inner member, wherein the inner member and the member to be joined are integrally joined by fastening means, A wheel mounting flange is provided on one of the outer or inner member and the member to be coupled, and a preload is applied to the bearing, and the inner member and the member to be coupled are fixed to a predetermined shaft by the fastening means. It is characterized by being united by force or more. When the present invention is applied to, for example, a bearing device for a front wheel on the driving side of a front-wheel drive vehicle, the member to be coupled is an outer joint member of a constant velocity universal joint. In addition, the present invention is applicable not only to rotating the inner member but also to rotating the outer member.

By applying a preload to the bearing, the rigidity of the bearing itself is increased, and the inner member and the member to be joined are integrally connected with each other by a fastening means with a predetermined axial force or more. This increases the coupling force (axial force) with the member. Thereby, when the vehicle turns, even if a load in the opposite direction to the axial force is generated due to a moment load or the like, since a predetermined axial force or more is present, there is no play at the joint thereof. As a result, surface runout of the brake rotor can be suppressed.

In the present invention, a preload is applied to the bearing. The preload of the bearing is 981 to 9810N (100 to 100N).
It is desirable to be 1000 kgf). If the preload amount is less than 981 N (100 kgf), it becomes difficult to increase the rigidity of the bearing alone, and the bearing clearance affects the brake rotor surface runout. Conversely, the preload amount is 981
If it is larger than 0N (1000 kgf), the rigidity of the bearing alone can be increased, but the load on the bearing increases accordingly, so that excessive preload causes a reduction in the life of the bearing. Also,
It is preferable that the axial force for integrally connecting the inner member and the member to be connected by the fastening means be 9810 N (1000 kgf) or more.

Further, the present invention provides a motor vehicle wherein the brake rotor is mounted on the wheel mounting flange, wherein when the brake rotor is rotated with reference to one of the outer member and the inner member, a fixed side member. It is desirable that the run-out width of the brake rotor be regulated to a standard value before the vehicle is assembled. Such a wheel bearing device with a brake rotor whose run-out width is regulated in advance is highly reliable, and the problem of surface run-out of the brake rotor is solved by directly using it at an automobile assembly plant. In addition,
It is desirable that the standard value of the swing width of the brake rotor be 50 μm or less.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a wheel bearing device according to the present invention will be described in detail below. INDUSTRIAL APPLICABILITY The present invention is applied to a bearing device that rotatably supports a driving-side front wheel of an FF (front-wheel drive) vehicle or a driven front wheel of an FR (rear-wheel driving) vehicle on a vehicle body. The present invention is applied to a front wheel bearing device of an FF vehicle or an FR vehicle. When the vehicle turns, even if a load in a direction opposite to the axial force is generated due to a moment load or the like, the runout of the brake rotor is suppressed. It depends on being able to show the effect.

FIG. 1 shows an embodiment of the present invention, which shows a bearing device for a driving-side front wheel in an FF vehicle. The bearing device of this embodiment includes a hub wheel 1 (an inner member in the claims) and an outer joint member 3 of the constant velocity universal joint 2 (a member to be joined in the claims).
And the bearing 4 are unitized. The outer joint member 3 of the constant velocity universal joint 2 has a stem portion 5 extending in the axial direction inserted into the through hole 6 of the hub wheel 1, and is formed at the outer diameter of the stem portion 5 and the inner diameter of the through hole 6. The nuts 9 are connected to the hub wheel 1 by the serrations 7 and 8 so that torque can be transmitted.
(Fastening means in the claims).

The hub wheel 1 and the outer joint member 3 of the constant velocity universal joint 2 are integrally connected by a nut. However, the present invention is not limited to this. It is possible.

The constant velocity universal joint 2 includes an outer joint member 3, an inner joint member 11 attached to an end of a drive shaft 10, and tracks of the inner joint member 11 and the outer joint member 3. A plurality of torque transmitting balls 12 incorporated between the grooves, and a retainer 13 supporting the torque transmitting balls 12 between the outer spherical surface of the inner joint member 11 and the inner spherical surface of the outer joint member 3. It is configured.

This bearing device has a structure in which a hub wheel 1 is rotatably supported by a bearing 4, a wheel wheel (not shown) is fixed to the hub wheel 1, and a knuckle 1 is attached to the bearing 4.
4 and supported by a vehicle suspension system (not shown).

The bearing 4 has a double-row angular contact ball bearing structure.
Double rows of raceway surfaces 16 and 17 are formed on the inner diameter surface of the outer ring 15 (outer member in the claims), and the outer ring 15 is provided on the outer peripheral surfaces of the inner rings 20 and 21 pressed into the outer periphery of the end of the hub wheel 1. Double-row raceways 18 and 19 facing the raceways 16 and 17 are formed, and double-row rolling elements 22 and 23 are interposed between the raceways of the outer ring 15 and the inner races 20 and 21 to form rolling elements of each row. 22,2
3 is provided with a structure in which cages 3 are supported at equal intervals in the circumferential direction by cages 24 and 25.

On the outer periphery of the outer ring 15, a vehicle body mounting flange 2 is provided.
6 protrudes, and is fixed to the knuckle 14 by screwing a bolt 28 to female screws 27 formed at a plurality of locations on the flange 26 along the circumferential direction. In order to prevent foreign matter from entering the bearing 4 and leakage of grease filled therein, seals 29 and 30 are provided.
Is provided.

The hub wheel 1 has a wheel mounting flange 31, and hub bolts 32 for fixing the wheel wheel are mounted on the flange 31 at circumferentially equal positions. A brake rotor 33 is fixed to the wheel mounting flange 31 of the hub wheel 1 by the hub bolt 32.

In this embodiment, the preload is applied by tightening the nut 9 to make the bearing clearance of the bearing 4 negative. The preload amount of this bearing 4 is 981 to 9810 N (10
0 to 1000 kgf). If the amount of preload is less than 981 N (100 kgf), it becomes difficult to increase the rigidity of the bearing alone, and the bearing clearance affects the brake rotor 33 as a runout. Conversely, if the preload amount is greater than 9810 N (1000 kgf), the rigidity of the bearing alone can be increased, but the load on the bearing 4 increases accordingly, and an excessive preload causes a reduction in the life of the bearing 4. In addition, the setting of the preload amount of the bearing 4 sets an initial clearance before fitting, and determines an estimated preload amount in consideration of a decrease in the clearance due to the fitting and the like.

The rigidity of the bearing unit is increased by applying a preload to the bearing 4 and the hub wheel 1 is integrally connected to the outer joint member 3 of the constant velocity universal joint 2 with a predetermined axial force by tightening the nut 9. Thereby, the coupling force (axial force) between the hub wheel 1 and the constant velocity universal joint 2 is increased. The axial force for integrally connecting the hub wheel 1 to the outer joint member 3 of the constant velocity universal joint 2 with the nut 9 is 9810 N (1000 kg).
f) More preferably. Thereby, when the vehicle turns, even if a load in the opposite direction to the axial force is generated due to a moment load or the like, since a predetermined axial force or more is present, there is no play at the joint thereof. As a result, surface runout of the brake rotor 33 can be suppressed.

In order to suppress the surface runout of the brake rotor 33, not only the runout of the mounting surface of the brake rotor alone but also the flange runout of the hub wheel alone, the axial runout of the bearing 4 and an assembly error (misalignment) are detected. It is necessary to improve the accuracy of each component alone, increase the rigidity of the bearing alone as in the embodiment of the present invention, and further, move the hub wheel 1 to the outside of the constant velocity universal joint 2 as in the embodiment of the present invention. By increasing the axial force coupled to the joint member 3 by the nut 9, the above-mentioned surface runout of the brake rotor 33 is suppressed.

FIG. 2 shows two samples A and B of the bearing device.
Is a graph in which the numerical values of the runout width of the brake rotor 33 are plotted for each of the brake rotor alone (the rotor alone), after the press-fitting of the bearing, and after the attachment of the constant velocity universal joint (after the attachment of the CVJ), and FIG. The bar graph shows the numerical values of the run-out width of the brake rotor 33 after the press-fitting and after the attachment of the constant velocity universal joint (after the attachment of the CVJ).

When the nut is finally tightened by the nut 9 and an axial force is applied as in the embodiment of the present invention, the runout of the brake rotor 33 is greatly reduced. That is, the surface runout of the brake rotor 33 was about 75 μm before the axial load, but after the axial load, the surface runout of the brake rotor 33 was reduced to about 30 μm, and the rigidity of the entire unit was reduced. It is apparent that this greatly affects the runout of the rotor 33.

In this embodiment, the outer race 1 of the bearing 4 is
When the hub wheel 1 is rotated on the basis of the outer diameter of No. 5, the run-out width of the brake rotor 33 is regulated to a standard value before the automobile is assembled. It is desirable that the standard value of the swing width of the brake rotor 33 be 50 μm or less. Such a wheel bearing device with a brake rotor whose run-out width is regulated in advance is highly reliable, and the problem of surface run-out of the brake rotor 33 is solved by directly using it at an automobile assembly plant.

In order to prevent the occurrence of brake judder, it is necessary to reduce the surface runout of the brake rotor 33 to 50 μm or less when the bearing device is assembled. In the embodiment of the present invention, if the surface runout of the brake rotor 33 can be suppressed to, for example, about 30 μm even when the accuracy variation of each component is considered, the surface runout of the brake rotor 33 can be set to 50 μm or less. it can.

For example, in order to restrict the surface runout of the brake rotor 33 to within the standard value in a state where the wheel bearing device with the brake rotor is assembled, the outer ring 15 of the bearing 4 is fixed to a measuring table (not shown), Based on this fixed outer ring 15,
One rotation of the hub wheel 1 and the wheel mounting flange 3 at that time
The deflection width of the brake rotor 33 fixed to 1 is measured with a brake gauge 33 such as a dial gauge (not shown).
And the measurement can be performed. In addition,
Before assembling the wheel bearing device, that is, before assembling the hub wheel 1 and the bearing 4, the wheel mounting flange 31 of the hub wheel 1 is provided.
, The surface run-out of the brake rotor 33 may be regulated within a standard value with respect to the rotation axis of the hub wheel 1.

In the bearing device for the front wheel on the driving side of the front-wheel drive vehicle according to the embodiment, the inner raceway surfaces 18 and 19 of the bearing 4 are provided.
Are formed on the inner rings 20 and 21 separate from the hub wheel 1,
The present invention is not limited to this, and one inner raceway surface 18 (outer board side) of the bearing 4 may be formed to the outer diameter of the hub wheel 1 or the other inner raceway surface 19 of the bearing 4 may be formed.
The outer joint member 3 of the constant velocity universal joint 2 (the inner board side)
It can also be applied to a type formed with an outer diameter of.

FIG. 4 shows an embodiment of the present invention, which shows a bearing device for a driven front wheel in an FR vehicle. The same parts as those of the drive-side front wheel bearing device shown in FIG. 1 are denoted by the same reference numerals.

The bearing device of this embodiment has an outer ring 15 (outer member in the claims) integrally provided with multiple rows of raceways 16 and 17 on the inner periphery, a wheel mounting flange 31 at one end, and an outer ring at the other end. Inner rings 20, 21 in diameter (inner member in claims)
The hub wheel 1 (the member to be joined) in which double rows of raceway surfaces 18 and 19 facing the raceway surfaces 16 and 17 of the outer race 15 are formed by press-fitting, the outer race 15 and the inner races 20 and 21.
Rows of rolling elements 22, 2 interposed between the respective raceway surfaces
3 and cages 24, 25 interposed between the inner races 20, 21 and the outer race 15 and supporting the rolling elements 22, 23 in multiple rows at equal intervals in the circumferential direction for each row. In the illustrated example, a double-row angular contact ball bearing is used as the bearing 4.

The outer ring 15 is press-fitted into the knuckle 14 and fixed with a retaining ring 34. On the outside and inside of the bearing 4,
A seal 35 and a cap 36 are arranged to prevent intrusion of foreign matter from the outside and leakage of grease filled in the inside. Hub bolts 32 for fixing wheel wheels are attached to the wheel attachment flange 31 of the hub wheel 1 at circumferentially equal positions. A brake rotor 33 is fixed to a wheel mounting flange 31 of the hub wheel 1 by a hub bolt 32. The inner rings 20, 21 of the bearing 4 are press-fitted into the outer diameter of the end of the hub wheel 1, and the protruding end of the hub wheel 1 is fixed by a nut 9 (fastening means in the claims).

In this embodiment, the bearing clearance is set to a negative value by tightening the nut 9 to apply a preload, and the preload is applied to the bearing 4 to increase the rigidity of the bearing alone. As in the case of the front wheel bearing device of the FF vehicle described above,
The preload amount of the bearing 4 is 981 to 9810 N (100 to 1
000 kgf). This preload amount is 9
If it is less than 81 N (100 kgf), it becomes difficult to increase the rigidity of the bearing unit alone, and the bearing clearance affects the surface runout of the brake rotor 33. Conversely, the preload amount is 98
If it is larger than 10 N (1000 kgf), the rigidity of the bearing unit can be increased, but the load on the bearing 4 increases accordingly, so that an excessive preload causes a reduction in the life of the bearing 4.
In addition, the setting of the preload amount of the bearing 4 sets the initial clearance before the fitting, and takes into account the reduction of the clearance due to the fitting, and the like.
The estimated preload amount is determined.

The rigidity of the bearing unit is increased by applying a preload to the bearing 4, and the hub wheel 1 is integrally connected to the bearing 4 with a predetermined axial force by tightening a nut 9. To increase the coupling force (axial force). The axial force for integrally connecting the hub wheel 1 to the bearing 4 with the nut 9 is preferably 9810 N (1000 kgf) or more. Thereby, when the vehicle turns, even if a load in the opposite direction to the axial force is generated due to a moment load or the like, since a predetermined axial force or more is present, there is no play at the joint thereof. As a result, surface runout of the brake rotor 33 can be suppressed.

In order to suppress the surface run-out of the brake rotor 33, not only the run-out of the mounting surface of the brake rotor alone, but also the flange run-out of the hub wheel alone, the axial run-out of the bearing 4, the assembly error (misalignment) and the like. It is necessary to improve the accuracy of each component alone, increase the rigidity of the bearing alone as in the embodiment of the present invention, and further reduce the axial force that couples the hub wheel 1 to the bearing 4. By raising, the above-mentioned runout of the brake rotor 33 is further suppressed.

In the bearing device for the driven front wheel of the FR vehicle in the above embodiment, the inner raceway surfaces 18 and 19 of the bearing 4 are provided.
Are formed on the inner rings 20 and 21 separate from the hub wheel 1,
The present invention is not limited to this, and is also applicable to a type in which one inner raceway surface 18 (outer board side) of the bearing 4 is formed to the outer diameter of the hub wheel 1.

Here, the respective bearing devices of the driven rear wheel of the FF vehicle and the driving rear wheel of the FR vehicle are provided with the brake rotor 33 in the case of using the disc brake for the rear wheel.
Does not need to be as severe as in the case of the front drive wheel of the FF vehicle and the driven front wheel of the FR vehicle, and the influence of the brake vibration on the vehicle body vibration is small. Therefore, in this bearing device, the stem end portion (FF) of the outer joint member of the constant velocity universal joint is reduced so that the number of parts is small and the cost is reduced.
Plastically deforms the end of the hub wheel (for FR vehicles) and the hub wheel and the constant velocity universal joint (for FF vehicles)
And the hub wheel and the bearing (in case of FR car) are integrally connected.

As the fastening means, a constant velocity universal joint (F
It is preferable that the ends of the F wheel and the hub wheel (in the case of FR vehicle) are plastically deformed radially outward by pressurization with a cylindrical punch or the like. By this caulking, similarly to the case of the above-described front wheel bearing device, the bearing clearance is set to a negative value, a preload is applied to the bearing 4, and the rigidity of the bearing alone can be increased. The preload amount of the bearing 4 is 981 to 981.
0N (100 to 1000 kgf) is desirable.

This caulking is performed by plastically deforming the ends of the constant velocity universal joint (in the case of FF vehicles) and the hub wheel (in the case of FR vehicles) radially outward by pressing with a cylindrical punch or the like.
This may be performed by forming a recess at the end of the constant velocity universal joint (for an FF vehicle) and the end of a hub wheel (for an FR vehicle), and expanding the ends radially outward to perform plastic deformation.

In the bearing devices for the drive-side front wheel of the FF vehicle and the driven-side front wheel of the FR vehicle, the case where the fastening by the nut 9 is used as the fastening means as described above has been described. It is also possible to employ fastening means by caulking, and it is possible to apply a predetermined amount of preload and an axial force by this caulking.

[0040]

According to the present invention, the rigidity of the bearing unit is increased by applying a preload to the bearing, and the inner member and the member to be joined are integrally connected by a fastening means with a predetermined axial force or more. Thus, the bonding strength between the two can be increased. As a result, in addition to improving the accuracy of each component such as the runout of the mounting surface of the brake rotor alone, the flange runout of the hub wheel alone, the axial runout of the bearing, and the assembly error (misalignment), the rigidity of the bearing alone, The axial force with the member to be joined can be improved, the surface runout of the brake rotor can be further suppressed, and uneven wear of the brake rotor and brake judder can be easily completely prevented.

[Brief description of the drawings]

FIG. 1 is an embodiment of a wheel bearing device according to the present invention;
Sectional view showing a bearing device for a front drive wheel of a car

FIG. 2 is a characteristic diagram showing a runout of a brake rotor for two samples.

FIG. 3 is a bar graph showing brake rotor surface run-out before and after axial load on two samples.

FIG. 4 is a sectional view showing a bearing device for a driven front wheel of an FR vehicle according to the embodiment of the present invention;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Inner member or member to be joined (hub ring) 2 Constant velocity universal joint 3 Member to be joined (outer joint member) 4 Bearing 9 Fastening means (nut) 15 Outer member (outer ring) 16, 17 Track surface 18, 19 Track surface 20, 21 Inner member (inner ring) 22, 23 Rolling element 31 Wheel mounting flange

Continued on the front page F term (reference) 3J012 AB06 BB01 DB01 FB07 HB02 3J017 AA05 DA01 DB07 3J101 AA03 AA32 AA43 AA52 AA62 FA41 GA03

Claims (7)

[Claims] 1. An outer member having a plurality of rows of raceways on an inner periphery thereof, an inner member having a raceway surface opposed to each of the raceways, and an intermediate member interposed between the outer member and the inner member. The inner member and the member to be connected are integrally connected by fastening means, and a wheel mounting flange is provided on either the outer or inner member or the member to be connected. A wheel bearing device, wherein a preload is applied to the bearing, and the inner member and the member to be coupled are integrally coupled by the fastening means with a predetermined axial force or more. 2. The wheel bearing device according to claim 1, wherein the member to be coupled is an outer joint member of a constant velocity universal joint. 3. The preload amount of the bearing is 981 to 9810N.
The wheel bearing device according to claim 1 or 2, wherein (100 to 1000 kgf). 4. An axial force of 9810 N (1000 kg)
The wheel bearing device according to any one of claims 1 to 3, wherein f) or more. 5. When the brake rotor is mounted on the wheel mounting flange and the brake rotor is rotated with reference to one of an outer member and an inner member on a fixed side member, the brake rotor swings. The wheel bearing device according to any one of claims 1 to 4, wherein the width is regulated to a standard value before the assembly of the vehicle. 6. The wheel bearing device according to claim 5, wherein the standard value is 50 μm or less. 7. The wheel bearing device according to claim 1, wherein the fastening means plastically deforms an end of the member to be joined.